US3977195A - Method for conditioning the intake air of a supercharged, low-compression ratio diesel engine - Google Patents

Method for conditioning the intake air of a supercharged, low-compression ratio diesel engine Download PDF

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Publication number
US3977195A
US3977195A US05/484,212 US48421274A US3977195A US 3977195 A US3977195 A US 3977195A US 48421274 A US48421274 A US 48421274A US 3977195 A US3977195 A US 3977195A
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United States
Prior art keywords
engine
air
cylinder
cylinders
preheating
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Expired - Lifetime
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US05/484,212
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English (en)
Inventor
Bernard Treuil
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MAN Energy Solutions France SAS
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Societe dEtudes de Machines Thermiques SEMT SA
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Priority claimed from FR7336900A external-priority patent/FR2247625A1/fr
Priority claimed from FR7346749A external-priority patent/FR2256322A2/fr
Application filed by Societe dEtudes de Machines Thermiques SEMT SA filed Critical Societe dEtudes de Machines Thermiques SEMT SA
Priority to US05/660,978 priority Critical patent/US4096697A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0437—Liquid cooled heat exchangers
    • F02B29/0443—Layout of the coolant or refrigerant circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0412—Multiple heat exchangers arranged in parallel or in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/44—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs
    • F02B33/443—Heating of charging air, e.g. for facilitating the starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M31/00—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture
    • F02M31/02—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating
    • F02M31/04—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates generally to and has essentially for its subject matter a method of running an internal combustion engine preferably with reciprocating pistons, in particular of the fuel-injection and compression self-ignition or Diesel type having in particular a relatively low volumetric compression ratio of a magnitude ranging preferably between 8 and 12 and supercharged for example to a substantial extent at a supercharging ratio as high as 5 for instance and in particular a method of at least temporarily conditioning or treating the air supply for said engine at start and/or possibly also at low-load conditions or idling speed operation of the engine as well as means or a device for carrying out such a method.
  • the invention also relates to the various applications and uses resulting or deriving from practicing said process and/or working said device or means as well as to the systems, assemblies, arrangements, apparatus, machines, equipments, installations, stationary appliances or power plants, automotive vehicles and ships of any kind and like constructions provided with such devices.
  • the supercharged air is generally delivered by one or several exhaust gas-driven turbo-blowers or like turbine-driven boosters or air compressors discharging into the intake manifold of the engine and consisting generally each one of an air compressor or booster mechanically coupled to a turbine usually driven by the exhaust gases issuing from each exhaust manifold of the engine.
  • One main object of the invention is therefore to remove the aforesaid inconveniences while enabling thereby to increase the rated or maximum power of the supercharged Diesel engine for a given or same piston stroke displacement or swept volume, i.e. cylinder capacity thereof.
  • the invention provides an improved process of running a supercharged low volumetric compression ratio Diesel engine in particular at start and possibly also at low-load or partial load conditions of the engine, and in particular a method of conditioning the air supply whether precompressed or not, said process being characterized by the step consisting in temporarily preheating the air supply or feed before it enters or reaches or is compressed or used to support combustion for burning fuel in the combustion chambers of the engine or prior to fuel injection into the engine cylinders or to fuel being mixed with said air therein.
  • the method according to one embodiment of the invention is characterized in that it consists in selectively braking, reducing, hindering or impeding the flow rate of the exhaust gases in a manner for instance variable or adjustable at will, in particular by generating a head or pressure loss at any of at least one or several locations in their flow path, positioned between, on the one hand at least one or each engine cylinder and, on the other hand at least one or each exhaust outlet opening to the atmosphere through which said exhaust gases are exiting to the outside and discharged into the open air.
  • said forced reduction in flow rate or artificial impeding of the gas flow is produced in the flow path of said exhaust gases between at least one or each engine cylinder and its associated exhaust manifold or towards the outlet or downstream end portion or collective exit to the open air of at least one or each exhaust manifold, either before, i.e. upstream of, or after, i.e. downstream of each drive turbine for the air compressor of the supercharging turbo-blower.
  • This reduction of flow rate is thus produced for instance in the affluent gas stream between at least one or each engine cylinder and the confluence or junction point where said affluent stream meets the collective main gas stream flowing in particular in its associated exhaust manifold.
  • Such a pressure or head loss may be obtained for instance by variation and in particular reduction in the cross-section of free passageway of flow of the exhaust gases.
  • This arrangement is advantageous especially at start or during the engine cranking period since it causes a reduction in the emptying or drainage of the engine cylinders so that there remains residual air heated through compression within the cylinders which effects the desired heat contribution or supply to the supercharged air.
  • This reduction in flow rate is removed as soon as the engine has started but it may also be maintained possibly while being modulated continuously depending upon or according to the partial load conditions of the engine through a suitable preferably automatic for instance feed-back control or like follow-up system.
  • the preheating step is carried out by selectively injecting and burning fuel into and substantially directly within at least one air intake manifold of the engine for producing hot combustion gases and thus mixing the latter directly with the supercharged air supply fed into and within the intake manifold.
  • the combustion-supporting oxygen content of this gaseous mixture is high enough to effect a reliable ignition within the engine cylinders in particular at the start of the latter and once the engine is running, the aforesaid combustion may be stopped.
  • the aforementioned preheating step consists in selectively substituting an auxiliary heating medium for the cooling fluid.
  • This arrangement offers the advantage of preheating the air admitted into the cylinders when the effective supercharging pressure is zero or low (at start and during the idling speed condition or slow running period, respectively), whereas this preheating step is discontinued and this air is cooled in a conventional manner when the supercharging pressure is high.
  • the aforesaid preheating step consists in selectively replacing said coolant by an auxiliary heating fluid.
  • This arrangement exhibits the advantage of enabling the preheating of the engine proper before its start by using its own normal cooling circuit. As soon as the engine has begun to work and has become warm, the circulation of heating fluid may be stopped and the cooling circuit put again into normal operation.
  • the aforementioned preheating step consists in selectively confining and heating the ambient air of the environment where the engine is located, so as to thereby convey and transmit heat to the engine in particular through convection before its start. Once the engine is running and warm, such a heating of the outer atmosphere is discontinued.
  • the preheating step is keyed or phase-locked preferably in an automatic manner and follow-up relationship through servo-control or like feedback means with the instant operating conditions of the engine so as to vary the temperature of the supercharged air possibly in a substantially continuous manner as the inverse ratio of the instantaneous load or rotational speed of the engine and possibly as a function of the pressure of this air.
  • the invention advantageously provides automatic control for constantly keeping the air admitted into the engine cylinders at a temperature ranging between a minimum temperature enabling the ignition of the injected fuel at the end of the compression stroke when the engine is operating at reduced power and a maximum temperature allowing a suitable feed with air when the engine operates at full power or load at the maximum supercharging pressure.
  • the invention relates also to a device for carrying out the aforesaid process in particular in the case of an engine supercharged by at least one exhaust gas driven turbo-blower set, which is characterized by the provision of means for at least temporarily preheating the air supply before it enters or reaches or is compressed or used to support combustion for burning fuel in the combustion chambers of the engine or prior to fuel injection into the engine cylinders or to the fuel being mixed with said air.
  • An embodiment of the device according to the invention is characterized by at least one selectively adjustable member for variably braking or reducing the flow rate of the exhaust gases, positioned at any location in at least one duct or pipe-line connecting at least one or each engine cylinder to at least one or each outlet opening to the outside through which said exhaust gases are exiting or discharged to the open air.
  • one aforesaid selectively adjustble member is positioned either within at least one or each branch-pipe connecting at least one or each engine cylinder to its associated exhaust manifold or at some point towards the downstream collective egress end portion, opening to the atmosphere, of at least one or each exhaust manifold either before or after one or each turbine driving the air booster compressor of one supercharging turbo-blower set.
  • At least one fuel burner means is mounted on at least one intake manifold at a position located between the upstream end or inlet portion thereof and some point towards and preferably in the vicinity or on the side of the outlet of said aftercooler means.
  • said fluid coolant circuit comprises selectively controllable or actuated switching valve means connected to a circuit of a hot source of heating fluid for successively putting said cooling fluid circuit in direct communication through series connection with said circuit of said hot source of heating fluid or disconnecting same from the latter.
  • an enclosure surrounding or containing said engine and fitted with means for heating or receiving and introducing hot air into said enclosure.
  • the aforementioned various forms of embodiment may of course be used either separately, i.e. independently of each other or in any possible combinations with each other.
  • the latter comprises means for keying or phase-locking in a preferably automatic manner the operating members for controlling and adjusting or regulating the preheating means for the supercharging air to the actual operating or instant working conditions of said engine in follow-up relationship.
  • These automatic servo-control means may be associated or combined with each one of the aforementioned forms of embodiment of the device according to the invention.
  • the invention relates also to the new industrial product consisting of the supercharged low-compression ratio Diesel engine provided with at least one aforesaid device.
  • the invention brings about a significant progress, technical advance or improvement over the known prior state of the art and is of economical manufacture. Moreover it is very efficient and effective while exhibiting a high reliability.
  • FIG. 1 shows a partially sectional top view of a supercharged Diesel engine provided with almost all of the aforesaid forms of embodiment of the device according to the invention.
  • FIG. 2 is a similar but simplified view showing various modifications or alternative embodiments of the exhaust gas flow rate reducing means mounted at various locations of the exhaust gas flow path to illustrate multiple possibilities of practicing this principle of the invention.
  • the reference numeral 1 generally designates a Diesel engine with a plurality of cylinders 2, arranged for instance in line but which may be disposed according to any arrangement for example arranged in two V-shaped rows of cylinders.
  • This engine comprises at least one air intake manifold 3 connected to the various cylinders, respectively, through branch-pipes 4 and at least one exhaust manifold 5 connected to the various cylinders, respectively, through branch-pipes 6.
  • the engine 1 exhibits a relatively low volumetric compression ratio, i.e.
  • Each turbo-blower comprises an air booster or compressor 7a, 8a operatively connected mechanically to a drive turbine 7b, 8b driven by the exhaust gases.
  • the inlet or ingress 9 of the high-pressure turbine 7b is connected to the downstream end portion or outlet of the exhaust manifold 5 whereas its outlet or egress 10 is connected through a connecting duct 11 to the inlet 12 of the low-pressure turbine 8b the outlet 13 of which opens to the open air for instance through the medium of a nozzle, funnel, chimney-stack or flue 14.
  • the low-pressure air compressor 8a draws air in from the atmosphere through its inlet orifice 15 and discharges same through its outlet orifice 16 and through an interstage cooler 17 into inlet or sucking orifice 18 of the high-pressure air compressor 7a through the medium of connecting ducts 19, 20 connecting the air inlet and outlet of the interstage air cooler 17 to the outlet 16 of compressor 8a and to the inlet 18 of compressor 7a, respectively.
  • the air outlet 21 of compressor 7a is connected through a duct 22 to the inlet of an air aftercooler 23 the outlet of which is connected to the upstream end or inlet of the intake manifold 3.
  • the intermediate or interstage air cooler 17 and the air aftercooler 23 consist each one of a heat exchanger through which a stream of coolant, for example of cooling liquid, is flowing through forced circulation.
  • the guided path of travel of the coolant in each one of these heat exchangers consists of a piping arranged as coils or nests, bundles or clusters of tubes which is connected in series to a cold source of coolant which is advantageously liquid such as for instance water.
  • This cold source may consist either of a ventilated radiator or of a coolant tank or of a local cold running water distribution system the fluid of which is discharged or delivered under pressure by pumping or through gravity.
  • each air cooler 17, 23 may be either recovered by being returned to the cold source (for example to the tank) or rejected as a waste.
  • the respective coolant inlet and outlet pipes 24, 25 of the air cooler 17 are respectively connected in series through the feed and return ducts 26, 27 to the cold source 28.
  • the respective coolant inlet and outlet pipes 29, 30 of the air aftercooler 23 are respectively connected in series through the supply ducts 31, 31a and return ducts 32, 32a to the cold source 33.
  • the method according to a first embodiment of the invention for preheating the precompressed supercharging air fed into the intake manifold 3 when starting the engine from the standstill or when it is running at low-load operating conditions or with a reduced or slow rotational speed consists in preheating the air when it is flowing through the air aftercooler 23 instead of cooling same therein.
  • the feed of cool fluid to the air aftercooler 23 is replaced by a supply of hot fluid for example a hot liquid such as warm water so that the air cooler 23 is thus converted into an air heater.
  • the respective feed and return ducts 31, 32 desirably comprise each one a three-way valve 34, 35 between or across which are branched off in by-passing relationship on the one hand the cold source 33 through the respective supply and return ducts 31a, 32a and on the other hand a hot source 36 through the respective supply and return pipes 31b, 32b.
  • This hot source 36 may consist for example either of a hot water generating boiler or of a hot steam generator or of a local hot water distribution system or main for supplying hot water under pressure for instance through pumping.
  • valve system 34, 35 could possibly be mounted in such a manner as to be able to connect the hot fluid source 36 in series to the cooling circuit 29, 30 of the air cooler 23 without disconnecting the latter from the radiator 33 which would thus be continuously mounted permanently in series within the cooling circuit, i.e. being constantly connected to the respective inlet and outlet pipes 29, 30 of the air cooler 23.
  • Another method of preheating the supercharging air according to the invention in particular at the start of the engine consists in the use of a fuel burner 37 mounted on or close to the intake manifold 3 so as to inject the hot combustion gases directly into the intake manifold 3 so that they may blend with the supercharging air therein in order to preheat the latter thereby.
  • the engine case or cylinder block 2' comprises as usual a cooling circuit for cooling the cylinders generally by means of a liquid such as water the respective inlet and outlet pipes 38, 39 of which are connected in series to an outer cold source 40 through respective supply and return ducts 41, 42.
  • the cold source 40 may consist for example of a heat exchanger such as a ventilated radiator or of a cold water tank or also of a local cold running water distribution system or main delivering cold running water discharged or supplied under pressure by pumping or through gravity into the feed or supply duct 41.
  • the hot water issuing from the pipe 39 may be either recovered and sent back to the cold source 40 or removed as a lost discharge or waste by means of the return line 42.
  • another process according to the invention consists in passing a hot fluid through the cooling circuit 38, 39 of the engine instead of the stream of cold water usually employed in order to preheat the engine cylinders hence the supercharging air entering same.
  • the pipes 38, 39 may be connected to the pipes 41, 42, respectively, through two three-way valves 43, 44, respectively, which are themselves connected in series through respective lines 45, 46 to a source 47 of hot fluid which may be either a liquid such as hot water or a gaseous fluid such as steam.
  • the hot source 47 may be a hot water generating boiler and in the latter case it may consist of a steam generator.
  • the system of valves 43, 44 could possibly be arranged so that it may connect the hot fluid source 47 in series to the cooling circuit 48, 49 of the engine without disconnecting the latter from the radiator 40 wich would thus be continuously interconnected in series permanently in the cooling circuit, i.e. being constantly connected to the respective inlet and outlet pipes 48, 49.
  • Still another method according to the invention for temporarily preheating the supercharging air at the start or under low-load operation of the engine consists in braking, impeding or reducing the flow of exhaust gases by temporarily introducing an obstacle or head pressure loss generating means into the downstream or outlet portion of the exhaust manifold 5 or advantageously at the outlet of the high-pressure turbine 7b.
  • This exhaust gas flow reducing means may consist of an element reducing or restricting the free cross-sectional passageway of flow and temporarily positioned or introduced into the duct 11 after the outlet 10 of the turbine 7b.
  • This member reducing, restricting or throttling the cross-sectional passageway may consist of a valve or movable closing member such as a pivoting flap, choke or strangler 48 permanently mounted within the duct 11 or also of a movable damper formed with at least one calibrated restriction passageway hole or the like.
  • the effect of the one or of the other of these partial closing members is to cause the engine cylinders to be incompletely emptied or drained so as to leave or retain therein residual air heated by compression and which in turn preheats the supercharging air being fed into the cylinders.
  • this partial closure of the exhaust is removed for example by moving the flap 48 to its fully open position or by entirely withdrawing the restriction or damper 49 formed with a throttling hole.
  • the flap 48 or movable apertured damper 49 may of course be located either before or upstream of the turbine 7b or at any location within the duct 11 or also after or downstream of the turbine 8b at the outlet 14 thereof.
  • the member 51 for selectively controlling the flow rate of the exhaust gases which may consist for instance either of a rotary valve member such as the throttle means 48 shown in FIG. 1 or of a movable damper 49 formed with a calibrated thoroughfare hole 49 also shown in FIG. 1, is inserted, according to a possible form of embodiment, within the downstream end of the exhaust manifold 5 of the engine where this control member 51 has been symbolically shown in solid lines by a rectangular block.
  • control member 51 may be interposed within one and preferably each one of the branch-pipes 6 connecting the cylinders 2 of the engine 1, respectively, to their associated exhaust manifold 5 as shown in broken or phantom lines by rectangular blocks inserted at an intermediate point of each exhaust branch-pipe 6, respectively.
  • control member 51 may be placed at the outlet 13 or towards the discharge opening 14 of the last turbine 8b driving the air compressor 8a of the supercharging turbo-blower set 8 or between two such successive turbines mounted in series, namely in the duct 11 connecting the outlet 10 of the upstream turbine 7b driving the air compressor 7a of the first supercharging turbo-blower set 7 to the inlet opening 12 of said second turbine 8b as shown in broken or phantom lines by rectangular blocks, respectively, in the drawing.
  • FIG. 1 a further method for temporarily preheating the supercharging air or the engine at the start thereof or when operating same under low-load conditions consists as shown in FIG. 1 in surrounding the engine 1 by a closed enclosure 50 consisting of the wall of a closed envelope such as a room, chamber or like compartment provided with means (not shown) for heating said enclosure, i.e. the ambient air confined thereby and bathing the engine 1.
  • the engine is thus heated through convection by this environmental hot atmosphere in particular before its start and then this heating may be discontinued.
  • turbo-blowers instead of using several (for instance two) supercharging turbo-blowers connected in series as in the illustrative embodiment shown it is of course possible to make use of one single turbo-blower only the air booster of which comprises for example several compression stages and the turbine of which possibly comprises several expansion stages.
  • the engine 1 may be cranked by a starter for example pneumatically or electrically powered.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Supercharger (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
US05/484,212 1973-10-16 1974-06-28 Method for conditioning the intake air of a supercharged, low-compression ratio diesel engine Expired - Lifetime US3977195A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US05/660,978 US4096697A (en) 1974-06-28 1976-02-24 Method and means for conditioning the intake air of a supercharged, low-compression ratio diesel engine

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR7336900A FR2247625A1 (en) 1973-10-16 1973-10-16 Conditioning of diesel engine's inlet air - involves precompressing flow by controlled interruption of supply
FR73.36900 1973-10-16
FR7346749A FR2256322A2 (en) 1973-12-28 1973-12-28 Conditioning of diesel engine's inlet air - involves precompressing flow by controlled interruption of supply
FR73.46749 1973-12-28

Related Child Applications (1)

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US05/660,978 Continuation-In-Part US4096697A (en) 1974-06-28 1976-02-24 Method and means for conditioning the intake air of a supercharged, low-compression ratio diesel engine

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US3977195A true US3977195A (en) 1976-08-31

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JP (1) JPS5065713A (no)
BR (1) BR7407621D0 (no)
CH (1) CH579708A5 (no)
DD (1) DD113067A5 (no)
DE (1) DE2441873A1 (no)
DK (1) DK141260B (no)
ES (1) ES429453A1 (no)
FI (1) FI59461C (no)
GB (1) GB1482605A (no)
IN (1) IN142745B (no)
IT (1) IT1019687B (no)
NL (1) NL7411074A (no)
NO (1) NO147395C (no)
PL (1) PL114827B1 (no)
SE (1) SE408576B (no)

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US6397598B1 (en) * 2000-10-04 2002-06-04 Caterpillar Inc. Turbocharger system for an internal combustion engine
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US20040020204A1 (en) * 2002-08-01 2004-02-05 Callas James J. Cooling of engine combustion air
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US7201121B2 (en) 2002-02-04 2007-04-10 Caterpillar Inc Combustion engine including fluidically-driven engine valve actuator
US7204213B2 (en) 2002-05-14 2007-04-17 Caterpillar Inc Air and fuel supply system for combustion engine
US20070089416A1 (en) * 2002-05-14 2007-04-26 Weber James R Combustion engine including engine valve actuation system
US7222614B2 (en) 1996-07-17 2007-05-29 Bryant Clyde C Internal combustion engine and working cycle
WO2007061339A1 (en) * 2005-11-22 2007-05-31 Volvo Lastvagnar Ab Internal combustion engine with two-stage turbo charging system
US7252054B2 (en) 2002-05-14 2007-08-07 Caterpillar Inc Combustion engine including cam phase-shifting
US7281527B1 (en) 1996-07-17 2007-10-16 Bryant Clyde C Internal combustion engine and working cycle
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US20140230430A1 (en) * 2013-02-19 2014-08-21 The Boeing Company Air Charge System and Method for an Internal Combustion Engine
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FR2835884A1 (fr) * 2002-02-12 2003-08-15 Valeo Thermique Moteur Sa Procede de controle de la temperature de gaz admis dans un moteur de vehicule automobile, echangeur et dispositif de gestion de la temperature de ces gaz
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US7310946B2 (en) 2003-07-31 2007-12-25 Behr Gmbh & Co. Kg Circuit arrangement for cooling charge air and method for operating a circuit arrangement of this type
CN100458116C (zh) * 2003-07-31 2009-02-04 贝洱两合公司 增压空气的冷却回路布置以及这种回路布置的运行方法
WO2005012707A1 (de) * 2003-07-31 2005-02-10 Behr Gmbh & Co. Kg Kreislaufanordnung zur kühlung von ladeluft und verfahren zum betreiben einer derartigen kreislaufanordnung
US20090217662A1 (en) * 2005-11-22 2009-09-03 Volvo Lastvagnar Ab Internal combustion engine with two-stage turbo charging system
WO2007061339A1 (en) * 2005-11-22 2007-05-31 Volvo Lastvagnar Ab Internal combustion engine with two-stage turbo charging system
US8333073B2 (en) 2005-11-22 2012-12-18 Volvo Lastvagnar Ab Internal combustion engine with two-stage turbo charging system
DE102007024633A1 (de) * 2007-05-24 2008-11-27 Behr Gmbh & Co. Kg Mehrstufige Verdichtereinheit mit Kühleinrichtung
US20090004029A1 (en) * 2007-05-24 2009-01-01 Behr Gmbh & Co. Kg Multistage compressor unit with cooling device
US8459961B2 (en) 2007-05-24 2013-06-11 Behr Gmbh & Co. Kg Multistage compressor unit with cooling device
US20090139473A1 (en) * 2007-12-04 2009-06-04 Mcmillan George Erik Engine fluid cooler
US8267054B2 (en) * 2007-12-04 2012-09-18 Mcmillan George Erik Engine fluid cooler
US20140230430A1 (en) * 2013-02-19 2014-08-21 The Boeing Company Air Charge System and Method for an Internal Combustion Engine
US9010114B2 (en) * 2013-02-19 2015-04-21 The Boeing Company Air charge system and method for an internal combustion engine
US20140251252A1 (en) * 2013-03-11 2014-09-11 Mazda Motor Corporation Compression self-ignition engine

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DK141260B (da) 1980-02-11
JPS5065713A (no) 1975-06-03
NL7411074A (nl) 1975-04-18
GB1482605A (en) 1977-08-10
SE408576B (sv) 1979-06-18
SE7412549L (no) 1975-04-17
IT1019687B (it) 1977-11-30
ES429453A1 (es) 1977-01-16
CH579708A5 (no) 1976-09-15
NO147395B (no) 1982-12-20
DK141260C (no) 1980-08-04
PL114827B1 (en) 1981-02-28
FI59461B (fi) 1981-04-30
FI302074A (no) 1975-04-17
BR7407621D0 (pt) 1975-09-09
FI59461C (fi) 1981-08-10
NO147395C (no) 1983-03-30
NO743662L (no) 1975-05-12
IN142745B (no) 1977-08-20
AU7107974A (en) 1976-01-15
DD113067A5 (no) 1975-05-12
DE2441873A1 (de) 1975-06-19
DK540274A (no) 1975-06-16

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